US4452566A - Reactive impeller for pressurizing hot flue gases - Google Patents
Reactive impeller for pressurizing hot flue gases Download PDFInfo
- Publication number
- US4452566A US4452566A US06/273,346 US27334681A US4452566A US 4452566 A US4452566 A US 4452566A US 27334681 A US27334681 A US 27334681A US 4452566 A US4452566 A US 4452566A
- Authority
- US
- United States
- Prior art keywords
- impeller
- flue gases
- hot flue
- cooling
- hub
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
- 239000003546 flue gas Substances 0.000 title claims abstract description 63
- 239000012809 cooling fluid Substances 0.000 claims abstract description 23
- 238000001816 cooling Methods 0.000 claims description 30
- 238000012546 transfer Methods 0.000 claims description 10
- 238000006243 chemical reaction Methods 0.000 claims description 5
- 238000007789 sealing Methods 0.000 claims 2
- 239000007789 gas Substances 0.000 abstract description 17
- 239000003570 air Substances 0.000 description 25
- 239000012530 fluid Substances 0.000 description 19
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 description 18
- 238000002485 combustion reaction Methods 0.000 description 10
- 238000013461 design Methods 0.000 description 8
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 8
- PXHVJJICTQNCMI-UHFFFAOYSA-N Nickel Chemical compound [Ni] PXHVJJICTQNCMI-UHFFFAOYSA-N 0.000 description 6
- 238000004519 manufacturing process Methods 0.000 description 6
- 238000000034 method Methods 0.000 description 6
- 238000010438 heat treatment Methods 0.000 description 5
- 230000008569 process Effects 0.000 description 5
- 230000000979 retarding effect Effects 0.000 description 5
- 229910045601 alloy Inorganic materials 0.000 description 4
- 239000000956 alloy Substances 0.000 description 4
- 239000000376 reactant Substances 0.000 description 4
- 229910000851 Alloy steel Inorganic materials 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 3
- 239000000446 fuel Substances 0.000 description 3
- 238000011084 recovery Methods 0.000 description 3
- 230000003068 static effect Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 229910001293 incoloy Inorganic materials 0.000 description 2
- 239000003345 natural gas Substances 0.000 description 2
- 229910052759 nickel Inorganic materials 0.000 description 2
- 230000037361 pathway Effects 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 239000012080 ambient air Substances 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 229910052804 chromium Inorganic materials 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 230000001747 exhibiting effect Effects 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000011159 matrix material Substances 0.000 description 1
- 239000000155 melt Substances 0.000 description 1
- 229910001235 nimonic Inorganic materials 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000001141 propulsive effect Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 229910052721 tungsten Inorganic materials 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
- F04D29/584—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling or heating the machine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/04—Units comprising pumps and their driving means the pump being fluid-driven
- F04D25/045—Units comprising pumps and their driving means the pump being fluid-driven the pump wheel carrying the fluid driving means, e.g. turbine blades
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/38—Blades
Definitions
- This invention relates to a means of pressurizing hot flue gases so that the gases can be moved through a heat recovery device and more specifically, to a reactive impeller for pressurizing hot flue gas.
- x 0.1
- a most effective preheating device is a continuously-operating recuperator.
- the gases have a near-zero static pressure.
- Conventional solutions for the problem thus presented are chimneys and eductors, i.e., jet pumps. These ordinary means of moving hot gases are grossly inefficient.
- the thermal efficiency of a chimney is generally a fraction of one percent.
- An unconventional solution would be a fan or blower, as commonly used for low temperature gases. Such a device would permit the use of a continuous heat recuperator and thereby surpass the thermal efficiency of the chimney by a ratio of about 100 to 1.
- the power produced by each device i.e., the generated pressure rise ⁇ P multipled by the volume flow rate V, ⁇ pV, is divided by the rate at which thermal energy is supplied to the system before it is upgraded to shaft power or the power of the entraining jet.
- An elementary calculation for each device is as follows.
- the efficiency ⁇ is as follows: ##EQU4## where c p is specific heat at constant pressure, Btu/lbm °F.; g c is a conversion factor 32.2 (lbm) (f)/lbf/sec 2 , ⁇ is density, lbm/ft 3 ; and T is absolute temperature.
- the Jet Pump The Jet Pump:
- the energy efficiencies of the three different means of pressurizing, or imparting momentum to, a hot stream of flue gas are in the ratio 1 to 30 to 100 (stack to jet pump to fan).
- a mechanically driven fan is clearly superior, were it not for the high temperatures involved.
- the fan or blower would have its blades present in the flue gases, at blade temperature of 2000° F. or more. Since even advanced and exotic turbine-blade alloys soften, flow and melt above 1750°-1800° F., the common fan could not withstand the heat of 2000° F. flue gases even if refined with exotic-blade alloys.
- Another object is to provide a pressurizing means which supplies sufficient pressure to the gas to permit use of a continuous heat recuperator and thereby improve upon the thermal efficiency of the chimney by a ratio of about 100 to 1.
- Still another object is to provide a pressurizing means which is continuous and scaled to pressurize the hot flue gases of continuous, industrial-scale, high temperature processes.
- a further object is to provide a pressurizing means which is economical of manufacture, operation and maintenance.
- the present invention is a reactive impeller for pressurizing hot flue gases comprising an impeller hub and impeller blades.
- the hub has an exterior hub surface and the blades have exterior blade surfaces, all of which are in contact with the hot flue gases.
- the exterior blade surfaces are shaped to propel the hot flue gases past the impeller upon rotational motion of the impeller.
- the hub defines a cooling chamber and cooling chamber inlet; the blades define cooling passages and nozzles.
- the chamber, inlet, passages and nozzles are all sealed from the hot flue gases and form a fluid pathway.
- the inlet opens to the chamber for introducing a cooling fluid to the cooling chamber, the passages open to the chamber for transfer of the fluid to the passages, and the nozzles open to the passages for expulsion of the fluid from the passages.
- the chamber receives the fluid from the inlet to cool the exterior hub surface, and the passages receive the fluid by transfer from the chamber to cool the exterior blade surfaces.
- the nozzles are directed to provide rotational driving motion to the impeller in reaction to expulsion of the fluid through the nozzles.
- the impeller is driven to pressurize the hot flue gases and the exterior surfaces are simultaneously cooled to withstand the hot flue gases by passage of the fluid through the impeller.
- FIG. 1 is a perspective view of the preferred embodiment of the invention in operation, positioned within a hot gas flue and a surrounding cooling fluid plenum.
- FIG. 2 is schematic view of the preferred embodiment of the invention, as used in a combustion reactant preheat system.
- FIG. 3 is a schematic view of a blade of the preferred embodiment of the invention, illustrating the principle of movement of the blade in reaction to expulsion of a cooling fluid.
- the preferred embodiment of the invention is a reactive impeller 10.
- the impeller has an impeller hub 12 and impeller blades 14.
- the impeller is located in a cylindrical hot gas flue 16, which is surrounded by a plenum 18.
- the hub 12 is centered in the flue 16 and tips 20 of the impeller blades 14 extend through an impeller blade opening 22 into the plenum 18.
- the flue 16 contains the hot flue gases of an industrial process, which have a temperature of 2000°-2200° F. or more and a static pressure, absent the impeller 10, of near-zero.
- the plenum 18 contains a cooling fluid which is a rectant of the industrial process.
- the flue 16 and plenum 18 are sealed from each other by a seal 24 which extends between the blades 14 about the opening 22.
- the seal 24 may be of a labyrinth type or any other suitable design.
- the hub 12 has a hub exterior surface 26.
- the blades have blade exterior surfaces 28.
- the surfaces 28 are defined as those portions of the surfaces of the blades 14 as are within the flue 16.
- the hub 12 and blades 14 have respective surfaces 26 and 28 exposed to the hot flue gases in the flue 16.
- the impeller 10 is adapted to provide movement, and hence pressure, of the hot flue gases in the flue 16, with minimum resistance.
- Arrow 30 represents the desired movement of the gases. Movement 30 is provided by the blades 14.
- the exterior surfaces 28 of the blades 14 are aerodynamically shaped. The shape is such that the blades 14 propel the gases through the flue 16 past the impeller 10 when rotated about the hub 12. Resistance to movement 30 is minimized by the hub 12.
- the exterior surface 26 of the hub 12 is aerodynamically shaped to provide a minimum resistance to movement of the gases.
- the impeller 10 acts by causing translational motion of the gases through the flue 16 in response to its own rotational motion.
- the impeller 10 is rotated by the cooling fluid.
- the hub 12 defines an internal fluid chamber 32 sealed from the hot flue gases, and a chamber inlet 34.
- the blades 14 define internal fluid passages 36 sealed from the hot flue gases, and nozzles 38.
- the inlet 34 oepns into the chamber 32 to introduce fluid to the chamber 32.
- the passages 36 open into the chamber 32 to transfer fluid in the chamber 32 to the passages 36.
- the nozzles 38 open into the passages 36 to expel fluid from the passages 36.
- the nozzles 38 are located on the blade tips 20, within the plenum 18.
- the nozzles 38 are directed to provide rotational propulsion to the impeller 10 in reaction to expulsion of fluid from the passages 36 into the plenum 18.
- a pressurized fluid introduced at the inlet 34 moves through the fluid pathways of the chamber 32 and passages 36, exits the nozzles 38 and drives the impeller 10.
- the cooling fluid also cools the impeller 10 and is preheated as it moves through the chamber 32 and passages 36. That is, the chamber 32 is a cooling chamber internally adjacent the hub exterior surface 26 which provides heat transfer from the surface 26 to the fluid within the chamber 32.
- the passages 36 are cooling passages internally adjacent the blade exterior surfaces 28 which provide heat transfer from the surfaces 28 to the fluid within the passages 36. As a result, sufficient heat is transferred from the surfaces 26, 28 that the impeller 10, unlike conventional fans, survives in the hostile environment of the hot flue gases within the flue 16.
- the impeller 10 is supported for rotation upon a bearing 40.
- the hub 12 is mounted on the bearing 40, which is within the chamber 32.
- the fluid in the chamber 32 cools the bearing 40, thereby protecting the bearing 40 as well as the surface 26.
- the impeller 10 is adapted to be used with a continuous heat recuperator.
- a suitable arrangement with such a recuperator 42 is shown in FIG. 2.
- the cooling fluid enters the inlet 34 through an inlet tube 44, and exits the plenum 18 through the recuperator 42 and out an annulus 46.
- the hot flue gases move past the impeller 10 into the recuperator 42 and exit through a stack 48.
- Equation 1 defines the velocities in the system: the absolute velocity v of the cooling fluid (air) at the point of leaving the nozzles 38; velocity u of the air relative to the nozzles 38 (such as would be measured by an observer on the tip 20 of a rotating blade 14 holding a Pitot tube just outside a nozzle 38. Finally, rw is the circumference (tangential) velocity of a nozzle 38 itself.
- Equation 2 gives the change of the moment of momentum (equal, in a constant-speed operation, to the retarding torque, M ret , produced by the action of the impeller blade 14 on the flue gas and by the friction force of the bearing 40).
- Equation 3 states that the work done per unit time by the impeller 10 in moving the hot flue gas and in overcoming the bearing friction, M ret w (ft-lbf/sec, W) is equal to the power of the blade-tip jets, ⁇ pV, less the rate at which the kinetic energy of air is lost in expansion, -mv 2 /2g c .
- equation 4 The range of possible angular velocities w is calculated from an equation 4, obtained by eliminating u and v from equations 1, 2 and 3: ##EQU6## Conversely, having fixed the angular velocity, equation 4 may be used to solve for the pressure drop across the nozzles 38 needed to balance the retarding torque M ret .
- equation 4 restricts the pressure head developed at a nozzle 38, ⁇ p/ ⁇ , to the following domain:
- the nozzle air temperature varies depending on the degree of preheat the air receives in passing through the inlet tube 44, the hub 12 and on the number of passes (if any) within a blade 14.
- This impeller 10 can be described in terms of the dimensionless parameters of the fan design theory by:
- the ratio is ##EQU8##
- the 50% efficiency indicated is high, considering that the impeller 10 is not designed to operate at maximum torque but is coupled to a prescribed load.
- the high efficiency is ascribed to the fact that the propulsive moment of momentum is developed by the mass flow rate m of air. Acting as a fan, the impeller 10 moves a volume, i.e. approximately the same mass of very hot flue gas divided by its low, 2000° F. density.
- the recuperator 42 is designed to take 2" w.c. or less pressure drop while handling the following time-rates of heat capacity: ##EQU9##
- prior experience, trial-and-error, or computerized optimization are used to choose a heat-transfer matrix and to arrive at the recuperator size, given the thermal duty and the allowable pressure drop.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
f.sub.a =0.9-0.514+0.269=0.655
v=|u-rw| ft/s, m/s 1.
M=rmv/g.sub.c ft-lbf, N-m 2.
M.sub.ret w=ΔpV-(mv.sup.2 /2g.sub.c ft-lbf/s, W 3.
M.sub.ret /2rρA<Δp/ρ<M.sub.ret /rρA 5.
65.7<Δp<131.4 6.
Claims (2)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US06/273,346 US4452566A (en) | 1981-06-15 | 1981-06-15 | Reactive impeller for pressurizing hot flue gases |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US06/273,346 US4452566A (en) | 1981-06-15 | 1981-06-15 | Reactive impeller for pressurizing hot flue gases |
Publications (1)
Publication Number | Publication Date |
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US4452566A true US4452566A (en) | 1984-06-05 |
Family
ID=23043524
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US06/273,346 Expired - Fee Related US4452566A (en) | 1981-06-15 | 1981-06-15 | Reactive impeller for pressurizing hot flue gases |
Country Status (1)
Country | Link |
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US (1) | US4452566A (en) |
Cited By (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2582719A1 (en) * | 1985-05-31 | 1986-12-05 | Gen Electric | MEANS OF ENERGY TRANSMISSION |
EP0430394A1 (en) * | 1989-11-28 | 1991-06-05 | Copermill Limited | Hot gas blower |
US5607289A (en) * | 1990-02-05 | 1997-03-04 | Underwater Excavation Ltd. | Underwater excavation apparatus |
GB2310005A (en) * | 1996-02-09 | 1997-08-13 | Michael John Wheatley | Apparatus for energy transfer |
GB2348671A (en) * | 1999-04-10 | 2000-10-11 | Frank Iles | Ramjet-driven axial flow fan |
US6179554B1 (en) | 1999-10-29 | 2001-01-30 | Elvin A. Stafford | Low friction fluid bearing and turbine using same |
FR2830906A1 (en) * | 2001-10-11 | 2003-04-18 | Air Liquide | Stirrer for cryogenic fluids used in food refrigeration has gas fed through paddle nozzles to rotate it by reaction force |
WO2005024230A2 (en) * | 2003-09-04 | 2005-03-17 | University Of Utah Research Foundation | Rotary centrifugal and viscous pumps |
WO2006091854A2 (en) * | 2005-02-25 | 2006-08-31 | Jack A Dean | Turbine systems |
US20070031256A1 (en) * | 2005-06-28 | 2007-02-08 | Bowles John C | Centrifugal motor (CM) |
US20070201974A1 (en) * | 2000-09-05 | 2007-08-30 | Dev Sudarshan P | Nested core gas turbine engine |
US20110012370A1 (en) * | 2008-01-23 | 2011-01-20 | Cortes Julio | System for the transport of an ore pulp in a line system located along a gradient, and components of such a system |
US20110107774A1 (en) * | 2009-11-12 | 2011-05-12 | Linde Aktiengesellschaft | Self-Powered Refrigeration Apparatus |
US20110150665A1 (en) * | 2009-12-22 | 2011-06-23 | Nissan Technical Center North America, Inc. | Fan assembly |
US20110173991A1 (en) * | 2004-12-07 | 2011-07-21 | ReCoGen, LLC | Turbine Engine |
US20150308438A1 (en) * | 2014-04-23 | 2015-10-29 | Electric Torque Machines, Inc. | Self-Cooling Fan Assembly |
WO2018077811A1 (en) * | 2016-10-25 | 2018-05-03 | Engineering Center Steyr Gmbh & Co Kg | Module for a cooling system of a motor vehicle |
DE102018213074A1 (en) * | 2018-08-03 | 2020-02-06 | Bayerische Motoren Werke Aktiengesellschaft | Ventilation device for a motor vehicle, motor vehicle with a ventilation device, method for operating a ventilation device and method for producing a ventilation device |
US11480193B2 (en) * | 2017-10-20 | 2022-10-25 | Techtronic Power Tools Technology Limited | Fan |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1054758A (en) * | 1912-07-16 | 1913-03-04 | Sten Teodor Fornander | Propeller-fan. |
FR546294A (en) * | 1921-05-12 | 1922-11-04 | Compressed air blower | |
US2001529A (en) * | 1933-02-02 | 1935-05-14 | Dornier Claude | Rotor for helicopters |
US2395404A (en) * | 1939-10-18 | 1946-02-26 | Daniel And Florence Guggenheim | Aerial propulsion apparatus |
US2612021A (en) * | 1947-05-12 | 1952-09-30 | Zuhn Arthur Attwood | Continuous combustion type rotating combustion products generator and turbine |
US2759700A (en) * | 1950-02-04 | 1956-08-21 | Gen Motors Corp | Bearing cooling system |
GB794198A (en) * | 1955-03-04 | 1958-04-30 | Fairey Aviat Co Ltd | Improvements relating to helicopters |
US3689173A (en) * | 1970-12-08 | 1972-09-05 | Randolph J Morton | Jet propelled motor |
US4354801A (en) * | 1981-01-23 | 1982-10-19 | Coppus Engineerng Corporation | Reaction fan with noise suppression |
-
1981
- 1981-06-15 US US06/273,346 patent/US4452566A/en not_active Expired - Fee Related
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
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US1054758A (en) * | 1912-07-16 | 1913-03-04 | Sten Teodor Fornander | Propeller-fan. |
FR546294A (en) * | 1921-05-12 | 1922-11-04 | Compressed air blower | |
US2001529A (en) * | 1933-02-02 | 1935-05-14 | Dornier Claude | Rotor for helicopters |
US2395404A (en) * | 1939-10-18 | 1946-02-26 | Daniel And Florence Guggenheim | Aerial propulsion apparatus |
US2612021A (en) * | 1947-05-12 | 1952-09-30 | Zuhn Arthur Attwood | Continuous combustion type rotating combustion products generator and turbine |
US2759700A (en) * | 1950-02-04 | 1956-08-21 | Gen Motors Corp | Bearing cooling system |
GB794198A (en) * | 1955-03-04 | 1958-04-30 | Fairey Aviat Co Ltd | Improvements relating to helicopters |
US3689173A (en) * | 1970-12-08 | 1972-09-05 | Randolph J Morton | Jet propelled motor |
US4354801A (en) * | 1981-01-23 | 1982-10-19 | Coppus Engineerng Corporation | Reaction fan with noise suppression |
Cited By (31)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2582719A1 (en) * | 1985-05-31 | 1986-12-05 | Gen Electric | MEANS OF ENERGY TRANSMISSION |
US4758129A (en) * | 1985-05-31 | 1988-07-19 | General Electric Company | Power frame |
EP0430394A1 (en) * | 1989-11-28 | 1991-06-05 | Copermill Limited | Hot gas blower |
US5607289A (en) * | 1990-02-05 | 1997-03-04 | Underwater Excavation Ltd. | Underwater excavation apparatus |
GB2310005A (en) * | 1996-02-09 | 1997-08-13 | Michael John Wheatley | Apparatus for energy transfer |
GB2348671A (en) * | 1999-04-10 | 2000-10-11 | Frank Iles | Ramjet-driven axial flow fan |
GB2348671B (en) * | 1999-04-10 | 2003-03-19 | Frank Iles | Axial flow fan |
US6179554B1 (en) | 1999-10-29 | 2001-01-30 | Elvin A. Stafford | Low friction fluid bearing and turbine using same |
US20070201974A1 (en) * | 2000-09-05 | 2007-08-30 | Dev Sudarshan P | Nested core gas turbine engine |
US20100034640A1 (en) * | 2000-09-05 | 2010-02-11 | Sudarshan Paul Dev | Nested core gas turbine engine |
FR2830906A1 (en) * | 2001-10-11 | 2003-04-18 | Air Liquide | Stirrer for cryogenic fluids used in food refrigeration has gas fed through paddle nozzles to rotate it by reaction force |
WO2005024230A3 (en) * | 2003-09-04 | 2005-07-28 | Univ Utah Res Found | Rotary centrifugal and viscous pumps |
US20070059156A1 (en) * | 2003-09-04 | 2007-03-15 | University Of Utah Research Foundation | Rotary centrifugal and viscous pumps |
WO2005024230A2 (en) * | 2003-09-04 | 2005-03-17 | University Of Utah Research Foundation | Rotary centrifugal and viscous pumps |
US20110173991A1 (en) * | 2004-12-07 | 2011-07-21 | ReCoGen, LLC | Turbine Engine |
US9523277B2 (en) | 2004-12-07 | 2016-12-20 | ReCoGen, LLC | Turbine engine |
WO2006091854A2 (en) * | 2005-02-25 | 2006-08-31 | Jack A Dean | Turbine systems |
WO2006091854A3 (en) * | 2005-02-25 | 2009-04-30 | Jack A Dean | Turbine systems |
US20070031256A1 (en) * | 2005-06-28 | 2007-02-08 | Bowles John C | Centrifugal motor (CM) |
US20110012370A1 (en) * | 2008-01-23 | 2011-01-20 | Cortes Julio | System for the transport of an ore pulp in a line system located along a gradient, and components of such a system |
US8461702B2 (en) * | 2008-01-23 | 2013-06-11 | Siemens Aktiengesellschaft | System for the transport of an ore pulp in a line system located along a gradient, and components of such a system |
WO2011059615A1 (en) * | 2009-11-12 | 2011-05-19 | Linde Aktiengesellschaft | Self-powered refrigeration apparatus |
EP2499441A1 (en) * | 2009-11-12 | 2012-09-19 | Linde Aktiengesellschaft | Self-powered refrigeration apparatus |
EP2499441A4 (en) * | 2009-11-12 | 2014-10-29 | Linde Ag | Self-powered refrigeration apparatus |
US20110107774A1 (en) * | 2009-11-12 | 2011-05-12 | Linde Aktiengesellschaft | Self-Powered Refrigeration Apparatus |
US20110150665A1 (en) * | 2009-12-22 | 2011-06-23 | Nissan Technical Center North America, Inc. | Fan assembly |
US20150308438A1 (en) * | 2014-04-23 | 2015-10-29 | Electric Torque Machines, Inc. | Self-Cooling Fan Assembly |
US9360020B2 (en) * | 2014-04-23 | 2016-06-07 | Electric Torque Machines Inc | Self-cooling fan assembly |
WO2018077811A1 (en) * | 2016-10-25 | 2018-05-03 | Engineering Center Steyr Gmbh & Co Kg | Module for a cooling system of a motor vehicle |
US11480193B2 (en) * | 2017-10-20 | 2022-10-25 | Techtronic Power Tools Technology Limited | Fan |
DE102018213074A1 (en) * | 2018-08-03 | 2020-02-06 | Bayerische Motoren Werke Aktiengesellschaft | Ventilation device for a motor vehicle, motor vehicle with a ventilation device, method for operating a ventilation device and method for producing a ventilation device |
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